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EP1320689A1 - Palier a embase soude, son procede de production et dispositif pour l'execution de ce procede - Google Patents

Palier a embase soude, son procede de production et dispositif pour l'execution de ce procede

Info

Publication number
EP1320689A1
EP1320689A1 EP01986333A EP01986333A EP1320689A1 EP 1320689 A1 EP1320689 A1 EP 1320689A1 EP 01986333 A EP01986333 A EP 01986333A EP 01986333 A EP01986333 A EP 01986333A EP 1320689 A1 EP1320689 A1 EP 1320689A1
Authority
EP
European Patent Office
Prior art keywords
bearing
thrust washer
bearing shell
flange
shell
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01986333A
Other languages
German (de)
English (en)
Other versions
EP1320689B1 (fr
Inventor
Hans-Jürgen KLIER
Klaus Kirchhof
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Federal Mogul Wiesbaden GmbH
Original Assignee
Federal Mogul Wiesbaden GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE10048256A external-priority patent/DE10048256A1/de
Application filed by Federal Mogul Wiesbaden GmbH filed Critical Federal Mogul Wiesbaden GmbH
Publication of EP1320689A1 publication Critical patent/EP1320689A1/fr
Application granted granted Critical
Publication of EP1320689B1 publication Critical patent/EP1320689B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/046—Brasses; Bushes; Linings divided or split, e.g. half-bearings or rolled sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/14—Special methods of manufacture; Running-in
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02—Crankshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/30—Material joints
    • F16C2226/36—Material joints by welding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y10T29/49643—Rotary bearing
    • Y10T29/49645—Thrust bearing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49636—Process for making bearing or component thereof
    • Y10T29/497—Pre-usage process, e.g., preloading, aligning
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/53—Means to assemble or disassemble
    • Y10T29/53104—Roller or ball bearing

Definitions

  • the invention relates to a flange bearing with a bearing shell and at least one thrust washer, the at least one thrust washer being fastened to an outer circumferential surface of the bearing shell.
  • the invention relates to a method for producing a flange bearing with a bearing shell and at least one contact washer, the at least one contact washer being fastened to an outer circumferential surface of the bearing cup.
  • the invention relates to a tensioning device, in particular a tensioning device for performing the production method mentioned.
  • flange bearing is used as a collective term for flange bearing half-shells and bushes, so that the bearing shell can be understood both as a bearing half-shell and as a cylindrical or tubular socket, the thrust washer being designed in the form of a ring or segment of a ring corresponding to the bearing shell , If the thrust washer is in the form of a ring, there is usually a closed ring or an almost closed ring with a joint.
  • Such flange bearings are used for numerous applications, in particular for the storage of highly loaded, fast rotating and wear-free Bearing shafts, such as crankshaft and / or camshaft of an internal combustion engine.
  • These flange bearings have a bearing shell and at least one thrust washer, which is attached to the left and / or right edge of the outer circumferential surface of the bearing shell.
  • the bearing shell serves to absorb radial bearing forces which are introduced via the shaft rotating in the bearing shell, whereas the at least one thrust washer serves to absorb axial forces. If axial forces are to be absorbed in both directions of the shaft, two thrust washers must be provided, since one thrust washer is only able to absorb the forces which are applied to its sliding layer. Cheeks are to be provided on the shaft, by means of which the shaft is supported on the at least one thrust washer.
  • crankshaft cranking As a result of the crankshaft cranking, the bearings for the crankshaft bearing in the crankcase are generally divided, although closed bearings and dismountable crankshafts could in principle also be used.
  • the flange bearings usually used for the axial and radial mounting of a crankshaft consist of a semicircular bearing shell and at least one thrust washer corresponding to it, which is fastened on the outer circumferential surface on the end face of the bearing shell to absorb the axial bearing forces.
  • Two such collar bearings result in a crankshaft bearing. They are accommodated in a bearing bore arranged in the crankcase, which is also divided and each semicircular.
  • a semicircular bearing shell is received by a corresponding semicircular recess in the so-called bearing saddle or in the bearing cap, with at least one additional one Recess for receiving and fixing the at least one thrust washer must be provided.
  • the need to provide recesses for receiving the thrust washers results from the fact that the thrust washers are usually only loosely or permanently connected to the bearing shell or multi-part flange bearings are used, in which the bearing shell and at least one thrust washer separately in Crankcase to be mounted.
  • flange bearings designed in one piece are usually used for mounting camshafts in internal combustion engines. These flange bearings have a tubular bushing, on the end face of which a thrust washer is arranged. In principle, the flange bearings only have a thrust washer, since they are pressed into the bearing bore that receives them and must therefore have an accessible side that is not provided with a thrust washer, which permits such a joining process.
  • two bushings are generally provided for each bearing, one bushing being pressed into the bearing bore from the left and one bushing from the right.
  • DE-OS 25 28 576 discloses a collar bearing which has a semicircular bearing shell and a thrust washer connected to this bearing shell. Both the semicircular bearing shell and the thrust washer consist of a support body and a lining applied to the support body. The outer shell support body is connected to the thrust washer support body by spot welding at localized locations.
  • One of the support bodies preferably has radially directed tabs, which form the locally limited locations for the welded connection between the support bodies. The tabs are usually located on the thrust washer support body and slots are formed in the bearing shell support body for receiving one tab.
  • a rigid connection is formed by welding the tabs inserted into the slots on the end face of the bearing shell.
  • the primary purpose of this connection is to enable simple, preferably mechanical, assembly, whereas such a welded connection does not serve the purpose of ensuring a stable connection between the bearing shell and thrust washer during operation of the internal combustion engine.
  • DE 34 25 180 AI discloses a flange bearing that is very similar to this flange bearing, in which the bearing shell is also welded to the thrust washers.
  • the thrust washers which are referred to as shoulder half rings, are connected to the bearing shell by projection welding or capacitor discharge welding.
  • the shoulder half-rings are manufactured in such a way that the radius of their inner circumference in a central region corresponds to the radius of the corresponds to the outer circumference of the bearing shell.
  • the half rings preferably have projections for performing the projection welding and the bearing shell has recessed seating areas for receiving and welding the shoulder half rings.
  • the finished flange bearing has a bearing shell in which the half rings are connected to the end face of the bearing shell by spot welding.
  • the thrust washers loosen due to the axial forces introduced by the crankshaft. This is accepted, however, since the problem underlying this flange bearing was to create a bearing shell in which the connection between it and the shoulder flanges is sufficiently firm to enable mechanized assembly (see DE 34 25 180 AI, page 5, Line 10 ff).
  • the slightly obliquely arranged thrust washers have the result that the sliding surface on them to absorb the axial bearing forces and Support of the crankshaft on the crank webs are also not arranged perpendicular to the crank axis, but inclined to it. As a result, the thrust washers are not loaded evenly over their entire sliding surface, but only partially, which can lead to overloading with the result of material removal and bearing destruction, but also to a vibration breakage of the thrust washer.
  • welded flange bearings In addition to the welded flange bearings according to the prior art, in which the welded connection is generally not a permanent, but merely a welded connection that simplifies assembly, built-up flange bearings are also offered.
  • a collar bearing shell is disclosed in DE 199 24 854 Cl.
  • the semicircular bearing shells have holding recesses in the region of an axial edge section of the radial bearing part.
  • the holding tongues which project inwards and are arranged on the receiving disc, which is referred to as the axial bearing part, are introduced into these holding recesses.
  • At least one of the holding recesses is open-edged and has a bendable web that axially delimits the recess, which is bent after inserting the thrust washer into the bearing shell and realizes an undercut of the holding tongue and thus fixes the thrust washer to the bearing shell.
  • Such form-fit joined flange bearings have low dimensional accuracy due to the relatively loose, form-fitting connection as well as due to the deformations to be made to produce the form-fitting connection.
  • the implementation of a positive connection by deforming the components themselves is relatively time-consuming and therefore costly.
  • DE 198 23 316 A1 discloses a flange bearing in which the bearing shell consists of a tubular bush on which an annular thrust washer is welded in the form of a flange by means of laser welding.
  • Such bushings are used for the storage of camshafts in internal combustion engines.
  • these flange bearings generally only have a thrust washer, since they are pressed into the bearing bore that receives them and must therefore have an accessible side that is not provided with a thrust washer.
  • two bushings are usually provided for each bearing, one bushing being pressed into the bearing bore from the left and one bushing from the right.
  • the welded connection generated between the thrust washer and bushing is a permanent connection that not only serves as an assembly aid, but is also intended to ensure that the thrust washer is fixed during operation. Consequently, when using such bushings, there is no recess to accommodate the thrust washer in the bearing.
  • a disadvantage of the flange bearings designed in this way and manufactured according to the prior art is the inaccuracy of shape.
  • the inaccuracy of the shape is again caused by the heat introduced in the course of the welding process and the thermal stresses that result when the joined flange bearing cools, which means that the thrust washer in the manufactured and cooled flange bearing is not, as intended, perpendicular to the bearing axis of the flange bearing, but vef is moved.
  • the object of the invention to provide a collar bearing with a bearing shell and at least one thrust washer connected to the bearing shell, in which the bearing shell is permanently connected to the at least one thrust washer, so that the recess to be provided according to the prior art for receiving the at least one thrust washer can be dispensed with, the flange bearing should be as cost-effective as possible, in particular post-processing due to an inclined, non-vertical thrust washer being dispensed with.
  • Another object of the present invention is to provide a method for producing a flange bearing with a bearing shell and at least one thrust washer, with which the bearing shell is permanently connected to the thrust washer, so that the recesses for receiving the at least one thrust washer are unnecessary and which one enables the most cost-effective production of such collar bearings.
  • Another sub-object of the present invention is to provide a tensioning device, in particular a tensioning device for carrying out the above-mentioned production method.
  • the first subtask is solved by a collar bearing of the generic type, in which at least one thrust washer is permanently welded to the bearing shell in operation in a joint located between the outer circumferential surface of the bearing shell and an inner circumferential surface segment of the thrust washer, the weld seam only one in the axial direction Part of the joint runs and, without reworking, the angle between the at least one thrust washer and the outer circumferential surface of the bearing shell assumes a value of 90 ° + 50 '.
  • the flange bearing according to the invention provides a permanent weld connection between the bearing shell and the at least one thrust washer, the weld seam being arranged between the inner peripheral surface and the outer peripheral surface of the bearing shell.
  • the at least one thrust washer is held and fixed by the bearing shell by means of the weld seam formed, which is why no recesses have to be provided for receiving the at least one thrust washer in the crankcase, as a result of which the first part of the first subtask of the underlying task is solved.
  • the thrust washers are, so to speak, permanently attached to the bearing shell for operation.
  • the weld seam is expressly not intended as a mere assembly aid, but rather as a permanent weld seam, the weld seam running in the axial direction only over a partial area of the joint.
  • a material excretion is noticeable, for example, through drop-shaped excretions located on the peripheral surface of the bearing shell. These initially liquid precipitates, which cool down together with the rest of the flange bearing after the welding process and change to hard deposits, must be removed in the course of post-processing in order to ensure that the flange bearing fits well in the bearing bore.
  • the flange bearing according to the invention is designed from the outset such that the at least one thrust washer forms an angle of 90 ° + 50 'with the outer circumferential surface of the bearing shell. Since the thrust washer is already perpendicular to the bearing shell after the welding process or is only a tolerable deviation from the ideal value has a post-processing of the thrust washer to correct the misalignment of the thrust washer is not necessary.
  • the vertical or almost vertical position of the thrust washer is achieved by holding the thrust washer in position or inclined during the welding process, this measure being carried out in detail below in the context of the manufacturing method according to the invention to be explained below.
  • Embodiments of the flange bearing are advantageous in which the weld seam has a rear side and a front side and, on the back of the weld seam, an essentially parallel gap is formed between the outer circumferential surface of the bearing shell and the inner circumferential surface segment of the thrust washer.
  • the outer circumferential surface of the bearing shell and the inner circumferential surface segment of the thrust washer are essentially cylindrical in shape - and that there is an annular air gap between the bearing shell and the thrust washer loosely fitted onto this bearing shell.
  • the annular air gap can also have a width of only a few micrometers, as is the case, for example, if a clearance fit is provided between the bearing shell and the thrust washer.
  • the described embodiment is advantageous with regard to the manufacturing process, since the thrust washer can be inclined or pretensioned with less force for welding than if the thrust washer is firmly seated on the bearing shell. A certain mobility of the thrust washer on the bearing shell is also favorable for the movement of the thrust washer due to the cooling of the welded joint.
  • An essentially parallel gap on the rear side of the weld seam means that the thrust washer is essentially perpendicular to the outer circumferential surface of the bearing shell, ie the angle o assumes its preferred value. Furthermore, the formation of a gap is an indicator that the weld seam runs only over a partial area of the joint, which leads to the advantages mentioned above.
  • Embodiments of the flange bearing are advantageous in which the radius of the inner peripheral jacket segment of the thrust washer essentially corresponds to the radius of the outer peripheral jacket surface of the bearing shell over the entire periphery of the thrust washer.
  • This embodiment has a large usable joint, so that a weld seam can be formed almost over the entire circumference of the thrust washer. This increases the stability of the flange bearing and ensures a secure permanent connection of the at least one thrust washer on the bearing shell.
  • Embodiments of the flange bearing are advantageous in which the at least one thrust washer is laser welded to the bearing shell.
  • the generation of the weld seam arranged between the thrust washer and the bearing shell by means of laser welding has a positive influence on the flange bearing due to the special properties of the laser welding process and leads to a high quality flange bearing.
  • the laser welding process is a welding process that works without an input of additional welding material and is only satisfied with the heating of the parts to be joined.
  • the lack of material input the formation of a weld seam protruding to the outside is avoided, which is why the excess welding material, which may be disruptive and stand out, does not have to be removed by reworking. - ?
  • the laser welding process enables targeted, selective heat input into the joint, so that the areas adjacent to the joint, which are inevitably also heated unintentionally can be kept as small as possible.
  • the risk of a structural change in these areas and the risk that the bearing shell and the thrust washer change their shape or their geometric dimensions are thus minimized or avoided.
  • Embodiments of the flange bearing are advantageous in which the flange bearing is welded from the outside, so that the weld seam, which has a rear side and a front side, has its front side on the side facing the thrust washer lining.
  • Collar bearings which consist of a bearing shell and two thrust washers arranged on this bearing shell, can be manufactured more easily and cost-effectively if the weld seam or the weld seams are introduced from the outside.
  • This embodiment also has advantages in that the circumferential surface area of the bearing shell located on the rear side of the thrust washer is not affected by the welding process.
  • the flange bearing is received in the bearing bore via the outer circumferential surface of the bearing shell, so that the circumferential surface is a mating surface which generally has to have tight tolerances.
  • embodiments of the flange bearing in which the flange bearing is welded on the inside can also be advantageous, so that the weld seam, which has a rear side and a front side, has its front side on the side facing away from the thrust washer lining.
  • This embodiment is advantageous, for example, in the case of collar bearings which are constructed from a closed tubular bearing shell, ie a bushing, and an annular thrust washer, ie a thrust ring. Because the thrust ring only has to be welded on, the rear of the thrust ring is also easily accessible, two of which are on the socket Wrestling start cannot be expected. A possibly minor post-processing of the flange bushing, for example the removal of weld material, is accepted, whereas the post-processing required according to the prior art due to the inclination of the thrust ring is also avoided here.
  • Embodiments of the flange bearing are advantageous in which the bearing shell has at least one circumferential groove in the circumferential direction on an inner circumferential surface of the bearing shell, preferably at the edge thereof.
  • the reduction in the cross section of the bearing shell leads to an increase in the flexibility of the bearing shell, with the preferred arrangement of the grooves at the edge of the bearing shell promoting the cushioning of dynamic axial forces introduced into the thrust washer.
  • Embodiments of the flange bearing are advantageous in which the bearing shell has at least one groove on an inner circumferential surface of the bearing shell, preferably in the middle thereof. This groove preferably extends in the circumferential direction, i.e. in the direction of the crankshaft rotation and serves as a lubricating oil reservoir by absorbing lubricating oil.
  • embodiments are advantageous in which the two thrust washers at least partially extend beyond the bearing shell in the circumferential direction.
  • Thrust washers designed in this way, which are arranged, for example, in the lower crankcase part, grip the opposite upper housing part and can thereby fix or center the upper crankcase part relative to the lower crankcase part.
  • Embodiments of the flange bearing are advantageous in which the at least one thrust washer has grooves in its outer surface which intersect the outer surface in the manner of a secant. These grooves are required in order to create a sufficiently stable lubricating film on the sliding surface, i.e. the outer surface of the thrust washer, and to drain oil.
  • Embodiments of the flange bearing are advantageous in which the at least one thrust washer has punched-outs on its inner circumferential surface segment.
  • the radius of the inner circumferential surface segment should preferably coincide with the radius of the outer circumference of the bearing shell over essentially the entire inner circumferential surface segment.
  • the at least one thrust washer and the bearing shell are not connected via a single coherent weld seam, but rather via many segment-like weld seams located between two punched holes.
  • the punched holes provided increase the flexibility of the federal warehouse.
  • the at least one thrust washer is permanently welded to the bearing shell
  • the at least one thrust washer is maintained over its entire circumference at an angle a + e between the at least one thrust washer and the outer circumferential surface of the bearing shell, the setpoint angle between the at least one thrust washer and the outer circumferential surface of the bearing shell corresponding to and e being the lead angle, which is chosen such that it is compensated for after the welding process and removal of the reserve due to cooling.
  • the method according to the invention ensures maximum dimensional and dimensional accuracy.
  • the intermediate collar dimension Z which describes the distance between the two thrust washers (see FIG. 3), is an extremely important dimension for a collar bearing, since the collar bearing is supported in this area in a bearing bore or on a bearing block and for the axial play of the Narrow tolerances on the bearing block must be observed; For example, a tolerance window between 20 and 80 ⁇ m can be specified for a clearance fit.
  • thrust washers should be arranged parallel to each other and perpendicular to the peripheral surface of the bearing shell.
  • the production of thrust washers oriented as vertically as possible is with the state of the art Known methods not possible, so that post-processing of the not sufficiently vertical thrust washers is necessary.
  • this effect is now taken into account in the production by prestressing the thrust washer over its entire circumference by the lead angle e, the lead angle being selected such that it is compensated for after the welding process and removal of the lead due to cooling.
  • the method according to the invention thus provides for a compensation of the cooling effect by appropriately pretensioning the thrust washer.
  • the thrust washer is tilted outwards as part of the pretensioning when welding from the inside and vice versa, tilted inwards when welding from the outside.
  • the cheek dimension W which denotes the axial distance between the outer surfaces of the thrust washers (see FIG. 3), should also have close tolerances over the entire circumference and the height of the thrust washers.
  • the method according to the invention is also expedient.
  • At least one thrust washer extends over substantially the entire circumference of the thrust washer Bearing shell is welded on. This ensures a sufficiently firm connection of the bearing shell to the at least one thrust washer and a high stability of the flange bearing.
  • the inclination of the laser welding beam is primarily a protective measure with regard to the thrust washer lining applied to the thrust washer support body, which would otherwise be used in a manufacturing process that removes the bearing shell and the at least one thrust washer from the outside, i.e. from the front of the bearing shell, welded, could be attacked.
  • the thrust washer lining in the area of the inner circumferential surface segment of the thrust washer is chamfered or provided with a phase, so that access to the joint relevant to the method is simplified.
  • the laser beam must be formed with a sufficient width in the area of the joint, which can be ensured, for example, that the focus of the laser beam lies in front of the wedge-shaped gap.
  • process variants are also advantageous in which the laser welding beam is focused in such a way that the focus lies in the wedge-shaped gap.
  • This protective gas has two functions. On the one hand, as in conventional welding processes which use a protective gas, it serves to avoid oxidation by displacing the oxygen in the joint by introducing the protective gas. *
  • the blowing in of a protective gas serves for the targeted cooling of the areas located in the vicinity of the joint. Surprisingly, it has been shown that even the direct introduction of protective gas into the joint does not complicate the formation of the weld seam itself, but advantageously counteracts the undesired heating of the adjacent areas of the joint.
  • Process variants are advantageous in which the flange bearing is welded from the outside, so that the weld seam, which has a rear side and a north side, has its north side on the side facing the thrust washer lining.
  • the flange bearing is welded on the inside, so that the weld seam, which has a rear side and a front side, has its front side on the side facing away from the thrust washer lining.
  • the third subtask is solved by a tensioning device for prestressing at least one thrust washer, which has a receptacle, at least one clamping jaw and at least two tensioning elements, and in which the receptacle has a first recess for receiving a bearing shell, which can be tensioned by means of a first tensioning element, and the receptacle further has at least one second recess for receiving the at least one thrust washer, the recess being designed in such a way that the thrust washer has the entire circumference under one of the at least one clamping jaw and a second clamping element Angle a ⁇ e between the at least one thrust washer and the outer circumferential surface of the bearing shell can be prestressed, the nominal angle between the at least one thrust washer and the outer circumferential surface of the bearing shell corresponding to the lead angle, which is chosen such that it after the welding process and Cancellation of the reserve due to cooling is compensated.
  • FIG. 1 is a perspective view of a first embodiment of a flange bearing in the form of a flange bearing half-shell with a bearing shell and two thrust washers,
  • Fig. 2 is a side view of a second embodiment of a
  • Flange bearing in the form of a flange bearing half-shell with a bearing shell and two contact washers
  • FIG. 3 is a view of the collar half-shell shown in FIG. 2 along the section III - III,
  • Fig. 4 is an enlargement of the detail Y of that shown in Fig. 3
  • Fig. 5 is an enlargement of the detail Z of that shown in Fig. 4
  • Fig. 6 in side view a section of a non-welded
  • FIG. 7 is an enlargement of the detail shown in Fig. 6 of a
  • Fig. 8 is a side view of a third embodiment of a
  • Flange bearing in the form of a flange half-shell with a bearing shell and two thrust washers
  • FIG. 9 shows a first embodiment of a clamping device with a clamped bearing shell and clamped thrust washers in longitudinal section
  • Fig. 10 shows the embodiment of a shown in Fig. 9
  • FIG. 11 shows a first clamping jaw of the clamping device shown in FIG. 9 in longitudinal section
  • Fig. 12 the inclusion of the clamping device shown in Fig. 9 in
  • FIG. 13 shows the second clamping jaw of the clamping device shown in FIG. 9 in longitudinal section
  • Fig. 14 shows the detail Z, the first clamping jaw shown in Fig. 11, and
  • Fig. 15 shows the detail Z 2 of the second shown in Fig. 13
  • Jaw. 1 shows a perspective view of a first embodiment of a collar bearing 1 in the form of a collar bearing half-shell with a bearing shell 2 and two thrust washers 3. Both the bearing shell 2 and the thrust washers 3 are coated, the bearing shell 2 comprising a bearing shell support body 2 'and one Bearing shell lining 2 "and the thrust washer 3 are constructed from a thrust washer support body 3 'and a thrust washer lining 3".
  • the radius of the inner circumferential jacket segment 13 of the thrust washer 3 corresponds to the radius of the outer circumferential circumferential surface 12 of the bearing shell 2 essentially over the entire circumference of the thrust washer 3.
  • the stop washers 3 have bevels only at their ends 7. Apart from this end area of the thrust washers 3, in which the bevels are located, the abutting washers 3 with the bearing shell 2 are in the usable joint by segment-like weld seams 8, which are between the outer circumferential surface area 12 of the bearing shell 2 and an inner circumferential surface area segment 13 of the thrust washer 3 is connected.
  • the flange bearing 1 is both stable and flexible.
  • the flexibility of the flange bearing is further increased by the grooves 4 on the edge of the inner peripheral surface of the bearing shell 3 in the circumferential direction.
  • the cross-section of the bearing shell 2 is reduced by the grooves 4, which increases the elasticity of the flange bearing 1.
  • the flange bearing 1 has a groove 6 in the bearing shell 2, which can serve to receive lubricating oil and, in addition, as a lubricating oil reservoir.
  • Grooves 5 are provided on the outer surfaces of the thrust washers 3, which are formed by the thrust washer lining 3 ′′ to form a load-bearing lubricating film in the axial sliding bearings formed by the thrust washers 3 and to remove oil.
  • FIG. 2 shows a side view of a second embodiment of a flange bearing 1 in the form of a flange bearing half-shell with a bearing shell 2 and two thrust washers 3.
  • This embodiment is similar to the collar half-shell shown in FIG. 1 and also has 3 bevels at the ends 7 of the thrust washers. Furthermore, this flange bearing half-shell also has grooves 4 running in the circumferential direction on the edge of the bearing shell 2.
  • this collar bearing half-shell has a coherent weld seam 8 ', which further increases its stability. So that the Anlau-fecheiben 3 are welded substantially over their entire Umfeng to the bearing shell 2.
  • FIG. 3 shows a view of the collar half-shell shown in FIG. 2 along the section 111-111.
  • the construction of the bearing shell 2 from a bearing shell support body 2 ′ and a bearing shell lining 2 ′′ applied to this support body can be clearly seen.
  • the grooves 4 arranged on the edges of the bearing shell 2 reduce the cross section of the bearing shell 2 on the end faces of the bearing shell 2 and thus increase it the flexibility of the bearing shell 2 and thus of the entire coil bearing 1.
  • a thrust washer 3 is arranged on the edges of the bearing shell 2, this thrust washer 3 being constructed from different materials in a manner similar to the bearing shell 2.
  • the thrust washers 3 have an inner thrust washer support body 3 'and one on this support body applied thrust washer lining 3 ", which, like the end face of the bearing shell 2, points outwards.
  • the intermediate collar dimension Z and the cheek dimension W are defined by the thrust washers 3 spaced apart on the bearing shell 2.
  • the intermediate collar dimension Z is the distance between the two thrust washers 3 in the direction of the flange bearing axis, i.e. as the distance between the two thrust washer support bodies 3 '.
  • the cheek dimension W is the distance between the two outer surfaces of the thrust washers 3 in the direction of the flange bearing axis. The cheek dimension W thus results as the sum of the intermediate collar dimension Z and the axial thickness of the thrust washers 3.
  • the two dimensions Z and W are closely tolerated dimensions that place high demands on the manufacturing process.
  • these dimensions must be as constant as possible over the height of the thrust washers 3, which can only be achieved in that the thrust washers 3 are arranged vertically on the bearing shell 2.
  • the thrust washers 3 should form an angle of 90 ° with the outer circumferential surface 12 of the bearing shell 2, as shown in FIG. 3.
  • FIG. 3 shows, in contrast to FIGS. 1 and 2, the weld 8 ′ in cross section.
  • the weld 8 ' is formed in a joint 10 which is arranged between the outer circumferential surface 12 of the bearing shell 2 and an inner circumferential surface segment 13 of the thrust washer 3.
  • This is the one shown in »Fig. 3 illustrated collar bearing half-shell around a collar bearing half-shell welded from the outside.
  • the weld 8 ' runs in the axial direction only over a partial area of the joint 10 and is triangular.
  • FIG. 4 shows an enlargement of the detail Y of the collar bearing half-shell shown in FIG. 3.
  • the support bodies 2 ', 3' of the bearing shell 2 or the thrust washer 3 are made of weldable material, usually steel, whereas the linings 2 ", 3" of both the thrust washer 3 and the bearing shell 2 generally consist of alloys, which are not weldable.
  • the weld seam 8 ′ extends in the axial direction only over a partial area of the joint 10, which is arranged between the bearing shell 2 and the thrust washer 3. As a result, an essentially parallel gap 9 forms on the rear side of the weld seam 8 '.
  • FIG. 4 Also shown in FIG. 4 is the angle et which the thrust washer 3 forms with the outer circumferential surface 12 of the bearing shell 2. This angle should ideally be 90 °, in practice a value of 90 ° + 50 '(minutes) is considered sufficient.
  • FIG. 5 represents an enlargement of the detail Z of the detail Y shown in FIG. 4.
  • the joint 10 is arranged between the outer peripheral surface 12 of the bearing shell 2 and an inner peripheral surface segment 13 of the thrust washer 3.
  • the outer contour of the bearing shell 2 or the bearing shell support body 2 'and the inner contour of the thrust washer 3 are substantially cylindrical, so that the rear 8'b Welding seam 8 'forms an essentially parallel gap 9 when the thrust washer 3 is fastened vertically on the bearing shell support body 2'.
  • the weld seam 8 ' extends only over a partial area of the joint 10.
  • the weld seam 8' which has a front side 8'a and a rear side 8'b, has an essentially triangular cross section, starting from the front side 8 'a tapered towards the back 8'b. 5 has been welded from the outside, so that the front 8'a of the weld seam 8 'lies on the side facing the thrust washer lining 3 ". It borders on one side with the thrust washer lining 3" and on the other side the end face 2'a of the bearing shell support body 2 '.
  • the weld axis 11 is slightly inclined in the direction of the bearing shell support body 2 ', which is due to the fact that the laser welding beam was not held perpendicular to the end face 2'a, but was also slightly inward.
  • the thrust washer lining 3 "in the area of the joint 10 is slightly chamfered or provided with a phase in order to make the joint 10 more easily accessible to the welding beam.
  • the beveling of the thrust washer lining 3" is intended to counter the risk that this will not weldable lining material is inserted into the weld 8 'during welding.
  • FIG. 6 shows a side view of a section of a non-welded flange bearing to illustrate the method step of holding the thrust washer 3 in place. Because the orientation of the thrust washer 3 changes after the weld seam has been introduced into the joint 10 as a result of the cooling, the lead angle e is inclined by the method according to the invention.
  • the thrust washer 3 must be tilted slightly inwards over its entire circumference, so that the thrust washer 3 forms an angle with the outer circumferential surface 12 of the bearing shell 2.
  • the lead angle e is selected such that the thrust washer 3 straightens up by this angle after the welding process and removal of the lead due to cooling. The lead angle e is thus a measure to compensate for the cooling effect and the inclination of the stop disc 3 caused by the cooling effect.
  • the provision of the thrust washer 3 is also formed in the joint 10 between the outer circumferential outer surface 12 of the bearing shell 2 and the inner circumferential outer surface segment 13 of the thrust washer 3 a wedge-shaped gap 17.
  • FIG. 7 shows an enlargement of the section of a flange bearing shown in FIG. 6 with a laser beam 15 directed into the joint 10 to illustrate the welding process.
  • the laser beam 15 is inclined inwards by the angle ⁇ and is focused in such a way that the focus 16 lies in front of the wedge-shaped gap 17 which is formed due to the thrust washer 3 being held in place. So that the cross section of the laser welding beam 15 is larger than the width of the wedge-shaped gap 17, so that the parts to be joined - the thrust washer lining 3 'and the bearing shell lining 2' - are heated to a sufficient extent.
  • 8 shows a side view of a third embodiment of a flange bearing in the form of a flange bearing half-shell with a bearing shell 2 and two thrust washers 3.
  • the thrust washers 3 of this embodiment have cutouts 14 on their inner circumferential surface segment 13. These punched-outs 14 have a uniform design and are regularly distributed over the inner contour of the thrust washers 3. As a result of the punched-out 14, the thrust washer 3 can only be connected to the bearing shell 2 via segment-like welds 8, a segment-like welded seam 8 being arranged in each case between two punched-outs 14.
  • the punched-outs 14 increase the flexibility of the coil bearing.
  • Such flange bearings are particularly suitable for applications in which the flange bearings are exposed to constant vibrations, which can be better cushioned or compensated for in this way.
  • FIG. 9 shows in longitudinal section a first embodiment of a clamping device 18.
  • the clamping device 18 has a receptacle 19 and two clamping jaws 20, 21. Furthermore, the clamping device 18 has two clamping elements 22, 23.
  • the clamping device 18 is fastened to a clamping plate 28 via two bolts 26, the two bolts 26 being received by two bores 27 and these bores 27 penetrating both the clamping plate 28 and the entire clamping device 28, i.e. proceeding from the clamping plate 28 via the second clamping jaw 20 and the receptacle 19 to the first clamping jaw 21.
  • a bearing shell 2 is arranged in the receptacle 19 in a first recess.
  • two thrust washers 3 are arranged and clamped by means of the two clamping jaws 20, 21 and a clamping element 22.
  • Another clamping element 23 serves to fix the bearing shell 2 in the receptacle 19.
  • FIG. 10 shows the clamping device 18 shown in FIG. 9 in a side view and partially in section.
  • FIG. 10 also clearly shows the means with which the bearing shell 2 is clamped in the receptacle.
  • the bearing half-shell 2 inserted into the receptacle abuts at one end against a stop 23 ', which in the present exemplary embodiment is formed by a screw and a stop plate.
  • the bearing shell 2 thus inserted into the receptacle is then braced with the first clamping element 23 at its other end.
  • the figures 11, 12 and 13 illustrate the essential elements of the clamping device.
  • FIG. 11 shows the second clamping jaw 20 of the clamping device shown in FIG. 9 in longitudinal section. It has a part of the receptacle 22 'for the second clamping element, this receptacle being designed as a thread in the region of the second clamping jaw 20.
  • Fig. 12 shows the receptacle 19 of the clamping device shown in Fig. 9 in longitudinal section.
  • the receptacle 19 also has a part of the receptacle 22 'for the second clamping element, this receptacle 22' being designed as a through hole in the region of the receptacle 19.
  • the receptacle 19 has a first recess 24 for receiving a bearing shell. This recess 24 is in the form of a segment of a circle and corresponds to the outer shape of the bearing shell to be accommodated.
  • the receptacle 19 has two further recesses 25a, 25b for receiving thrust washers. These recesses 25a, 25b are arranged on the end faces of the receptacle 19 and open towards the end faces.
  • the end faces 25a ', 25b' of the recesses 25a, 25b are inclined relative to the vertical by the lead angle e.
  • the ends of an end face 25a ', 25b' each have an axial offset a of 0.05 mm.
  • annular thrust washer has an inner diameter of 70.1 mm and an outer diameter of 84.88 mm
  • an axial offset of 0.05 mm at the ends of the end face leads to a lead angle e of about half a degree or 30 minutes.
  • the axial offset a is also shown for both recesses 25a, 25b and for the two end faces 25a ', 25b' of these two recesses in FIG. 12.
  • FIG. 13 shows the first clamping jaw 21 of the clamping device shown in FIG. 9 in longitudinal section.
  • This clamping jaw 21 also has part of the receptacle 22 'of the second clamping element.
  • Figs. 14 and 15 show the details Z and Z 2 of FIGS. 11 and 13, respectively.
  • FIG. 14 shows the detail Z of the second clamping jaw 20 shown in FIG. 11 in an enlargement of 5: 1. It can be seen that the second clamping jaw 20 also has a recess 20a, which, however, has a smaller depth than the recesses of the receptacle 19 shown in FIG. 12.
  • the end face 20a ′ of the recess 20a is also inclined by the lead angle e with respect to the vertical.
  • the recess 20a of the second clamping jaw 20 extends by the same amount in the radial direction as the corresponding recess of the receptacle, then the axial offset a of the two ends of the end face 20a 'of the recess 20a is equal to the axial offset a of the end face of the recess of the receptacle.
  • the axial offset of the ends of the end faces 20a ', 21a', 25a ', 25b' of the recesses 20a, 21a, 25a, 25b is the same size and is 0.05 mm for the already mentioned embodiment.
  • FIG. 15 shows, corresponding to FIG. 14, the detail 2 of the first clamping jaw 21 shown in FIG. 13 in an enlargement of 5: 1.
  • FIG. 14 can be transferred to FIG. 15, the first clamping jaw 21 having a recess 21a and an end face 21a '.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Belt Conveyors (AREA)
  • Lining Or Joining Of Plastics Or The Like (AREA)

Abstract

L'invention concerne un palier à embase (1) pourvu d'une coquille de coussinet (2) et d'au moins une rondelle de butée (3) fixée sur une surface d'enveloppe périphérique externe (12) de la coquille de coussinet (2). L'invention concerne également un procédé pour la production d'un tel palier à embase (1) et un dispositif de serrage (18) pour l'exécution de ce procédé de production. L'invention vise à fournir un palier à embase (1) dans lequel la coquille de coussinet (2) est raccordée de manière permanente à la rondelle de butée (3). L'invention vise à présenter un procédé permettant de produire un tel palier à embase (1) le plus économiquement possible et rendant notamment inutile un réusinage dû à une rondelle de butée oblique et non verticale (3). L'invention concerne en outre un dispositif de serrage (18) pour l'exécution du procédé. L'invention concerne particulièrement un procédé selon lequel la rondelle de butée (3) est soudée de manière permanente à la coquille de coussinet (2) à un emplacement d'assemblage (10) situé entre une surface d'enveloppe périphérique externe (12) de la coquille de coussinet (2) et un segment de surface d'enveloppe périphérique interne (13) de la rondelle de butée (3). La rondelle de butée (3) est inclinée sur toute sa périphérie d'un angle alpha +/- ELEMENT entre la rondelle de butée (3) et la surface d'enveloppe périphérique externe (12) de la coquille de coussinet (2), alpha correspondant à l'angle nominal entre la rondelle de butée (3) et la surface d'enveloppe périphérique externe (12) de la coquille de coussinet (2) et ELEMENT étant l'angle d'inclinaison sélectionné de façon à être compensé après le soudage et la suppression de l'inclinaison en raison du refroidissement.
EP01986333A 2000-09-29 2001-10-01 Palier a embase soude, son procede de production et dispositif pour l'execution de ce procede Expired - Lifetime EP1320689B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10048256A DE10048256A1 (de) 2000-09-29 2000-09-29 Bundlager und Verfahren zu seiner Herstellung
DE10048256 2000-09-29
PCT/DE2001/003762 WO2002029269A1 (fr) 2000-09-29 2001-10-01 Palier a embase soude, son procede de production et dispositif pour l'execution de ce procede

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EP1320689A1 true EP1320689A1 (fr) 2003-06-25
EP1320689B1 EP1320689B1 (fr) 2005-12-07

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US (1) US7441958B2 (fr)
EP (1) EP1320689B1 (fr)
JP (1) JP2004510928A (fr)
AT (1) ATE312296T1 (fr)
BR (1) BR0114279A (fr)
DE (1) DE50108338D1 (fr)
ES (1) ES2253440T3 (fr)
WO (1) WO2002029269A1 (fr)

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See references of WO0229269A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007143987A1 (fr) * 2006-06-14 2007-12-21 Federal-Mogul Wiesbaden Gmbh Bague de roulement lisse axial

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WO2002029269A1 (fr) 2002-04-11
ATE312296T1 (de) 2005-12-15
DE50108338D1 (de) 2006-01-12
BR0114279A (pt) 2003-12-30
EP1320689B1 (fr) 2005-12-07
ES2253440T3 (es) 2006-06-01
JP2004510928A (ja) 2004-04-08
US7441958B2 (en) 2008-10-28
US20050223546A1 (en) 2005-10-13

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